Variable speed transmission



June 1943- w. L. OLLARD 2,322,251 I VARIABLE SPEED TRANSMISSION Filed Sept. 15, 1941 Patented June 22, 1943 UNITED STATES PATENT OFFICE,

VARIABLE SPEED TRANSMISSION Willard L. Pollard, Evanston, Ill. Application September 15, 1941, Serial No. 410,815

4 Claims. (Cl. hi-189.5)

My invention relates to variable speed transmissions.

' One of the objects of my invention is to provide a simple, inexpensive and effective form of three-speed hydraulic transmission.

Further objects and advantages of the invention will be apparent from the description and claims. 7

'In the drawing, in which several forms of my invention are shown.

Figure 1 is an axial sectional view showing a combination of hydraulic coupler and planetary; Fig. 2 is'an elevational view of the baflle or iiow controller shown in Fig. 1;

Fig. 3 is an axial sectional view showing a planetary construction which may be substituted for that shown in Fig. 1;

Fig. 4 is an axial sectional view showing a combination of hydraulic coupler, hydraulic torque converter and planetary; and

Fig. 5 is an axial sectional view showing another form of hydraulic coupler, hydraulic torque converter and planetary.

Referring to the drawing in detail, and first to Figs. 1, 2, and 3, the construction shown comprises a hydraulic coupler including a pump rotor i, rotatable with a drive rotor 2, a turbine rotor 3, and a flow-separation and torque-transmitting rotor t, a planetary construction including a sun gear 5 keyed to rotate with the shaft 6 to which the flow-separating rotod l is keyed. a ring gear l, a gear carrier 2. keyed to rotate with the driven shaft 9 and planetary shaft 8 and planetary gearing it meshing with the sun gear 5 and ring gear l, a multiple disc clutch II for connecting and disconnecting the hollow shaft 92 on which the turbine rotor 3 is carried with the hollow shaft it on which the outer shell of the flow-separating rotor 6 is keyed, a brake I4 for holding the drum E5 of the clutch against rotation when desired, a clutch it for connecting and disconnecting the ring gear 5 with respect to the hollow shaft W of the turbine rotor, and a brake i? for holding the ring gear l against rotation when desired. The flow-separating rotor is substantially open along an inner zone 88 opposite the inner ends of the blades of the pump and turbine rotors and is also open along an outer zone is opposite the outer ends of the blades of the pump rotor; and turbine rotor, narrow spokes 20, however, being provided for bridging across these zones for transmitting torque from the outer shell 28 of the rotor to the hub 22 secured to the shaft 8. Any suitable control means may be provided for controlling the operation of the clutches H and I6 and brakes l4 and I I.

For low speed, the brake I1 is applied to hold the ring gear 1 against rotation, the clutch I! is disconnected to free the ring gear from the turbine rotor, the brake I4 is released, and the clutch H is operated to connect the turbine rotor I with the torque-transmitting flow-separation rotor 4, and hence with the sun gear 5 through the shaft. With this arrangement, the ring gear I is held and power flows from the pump rotor I through the passages in the flowcontrol rotor I to the turbine rotor 3, through the sleeve l2, clutch ll, clutch sleeve l2, torque-transmitting rotor 4 and shaft 8 to the sun gear 5.

For second speed, the brake I4 is applied to hold the sun gear 5 against rotation, the clutch II is released, the brake II is released. and the clutch I6 is applied to connect the ring gear I with the sleeve 12 on which the turbine rotor I is mounted. Under these-conditions, the sun gear 5 is held against rotation by the brake l4 1 which holds the brake drum II, the torque-transmitting rotor 4, the shaft 6, and sun gear 5 against rotation, and the ring gear 'I rotates with the turbine rotor 3, the power flowbeing from the turbine rotor 3 through the sleeve l2 and clutch it to the ring gear I. For substantially direct drive, both brakes l4 and i! are released, and both clutches II and it are applied, thus connecting both the sun gear 5 and ring gear i with the turbine rotor 3.

It is obvious that one-way anchorage devices may be substituted for either or both. of the brakes l4 and ll with consequent free wheeling action.v A clutch plate Ila rotatable with the clutch sleeve l3 and engageable and disengageable with respect to the casing of the drive rotor I may be provided enabling the sun gear to be connected to rotate as a unit with the drive rotor I to by-pass part of the power around the ring gear l.

In Fig. 3 is shown a planetary unit which may be substituted for theplanetary unit shown in Fig. 1 and which enables 'a satisfactory reverse to be obtained. In this form, the sun gear 5, ring gear i, brake I1, and shaft 6 may be the same as in Fig. 1. In place, however, of the planetary gearing l0 shown'in'Fig. 1, a duplex planetary gearing 23 may be substituted, having one gear portion 26 which operates just as the gearing 10 shown in Fig. 1' operates but having an additional gear portion 25 of somewhat larger clutch constructionjlt The pump rotor .pler 36. the intermediate shaft 36 to torque exerted bydiameter than the gear portion 24 which meshes with sun gear 26. By means of a suitable dog clutch 21, the driven shaft 6 may beconnected so as to rotate either with the gear carrier 26 or with the sun gear26. When connected to rotate with the gear carrier 26, the operation is just as described in connection with Fig. 1. When, however, the clutch sleeve 21 splined on the driven shaft S'isshifted forwardly so that its dog clutch teeth 26 .will engage the sun gear 26 instead of the gear carrier 26, then, if the I clutchesand brakes are arranged so as to hold the sun gear-'5 against rotation and connect the ring gear 1 to rotate with the turbine rotor 3,

. the sun gear 26 will .be rotated in a direction reverse to the rotation of the ring gear I but at a lower speedwhichspeed. is determined by the relative pitch diameters of the two gear portions '24 and 25. of the duplex gear.

The constructionshown in Fig. 4'comprises a hydraulic coupleri 36', a hydraulic torque conand a 34 of 35 of verter 3|, a planetary gearconstruction 32,

the hydraulic coupler and thepump rotor the hydraulic, torque converter are both secured to rotate with'the drive shaft 36. The turbine rotor 31 of the coupler-and the. turbine rotor 36' of the converter areboth' keyed to rotate with an intermediate shaft36. I['|:ie-ring gear 46 may be connectedand disconnectedwith respect to the shaft 36 on whichtheturbinerotors 31 and 36 are keyed by ineansof the clutch 33. A one-way anchorage device 46a'is provided to prevent reverse rotation "of.the ring gear 32 when the clutch 33-isdisconnected. A one-way clutch 4| is provided to prevent the ring gear 46 from overrunning the turbine. rotor 36. A one-way anchorage device 42 isprovided to prevent re-, "verse rotation of the reaction stato rotor 43. A

one-way clutch 44 is provided to prevent the state rotor 43 from overrunriing the turbine rotor 36.

A one-way clutch 45 may be provided to prevent the intermediate shaft 36 from overrunning the] sun gear 46 and ring gear .46. This planetary" may be the sameas thatshown in Fig. 1. If desired, the planetary gear/construction shown in Fig. 3 may be substituted for that shown in Fig. 4. In operation, power is transmitted from the drive shaft 36 to the intermediate shaft 36 in parallel. one branch beingthrough the hydraulic coupler36 to the intermediate shaft and the other being through the hydraulic torque converter 3| to the intermediate shaft. With this construction, torque will beincreased in the branchthrough the torque converter 3|, but torque will not be increased in the branchthrough the cou- When the ratio of torque resistance in the pump rotor 35 reachesa certainvalue, the

stato rotor 43 will begin to rotate and the hydraulic torque ,converterwill then function as a hydraulic coupler; In n'general, a hydraulic torque converter does not act with great efflciency as a hydraulic coupler. .However, the coupling action after the transformation takes place is ththe transformed conr by the planetary transmission 32.

. For a lower torque, the clutch 33 is connected and both ring gear 46 and sun gear 46 are then direct connected to the intermediate shaft 36 so that the whole planetary turns as a unit and the driven shaft 46 rotates in unison with the intermediate shaft 36. v The construction shown in Fig. 5 comprises aplanetary gear construction 46, a brake 56; a twoway clutch 5|, a hydraulic coupler 52, and a hydraulic torque converter 53. The drive shaft, isconnected to rotate with the gear carrier 65 of the planetary. The driven-shaft 56 is connected'to rotate with the ring gear 51, the turbine rotor 56 of thehydraulic. coupler, and the turbine rotor 56 of the hydraulic torque converter.

'SI of the torque converter. The pump rotor-6| of the hydraulic torque converter'can-be coupled alternatively either with the gearcarrier 55 of converter 53.

the planetary orwith the sun gear of the planetary. The brake 56 may be applied to hold the sun-gearagainst rotation when desired to effect overdrive.

In operation, for high torque in the driven shaft'56. the clutch 5| is operated to connect the gear carrier of the planetary with the pump rotors 66 and 6| of'the coupler 52Jand torque Under these conditions, power flows in two parallel paths from the gear carrier 55 of the planetary to the driven shaft 56, one path being through the hydraulic coupler 52 and the other path being through the hydraulic torque converter 53, the operation and effect of this connection being substantially as described in connection with Fig. 4 for divided power flow.

For lower torque in the driven shaft 56; the pump rotors; 66 and 6| of the coupler 52 and torque converter 53 are disconnected from the gear carrier 55 and connected with the sun-gear '62. Un-

der these conditions, there isa three-way power path from thegear carrier .55 to the drivenshaft.

56. One path'is from the gear carrier 55 through the planet gearing 63 and ring gear 51 which is keyed to the driven shaft 56'. Another path is from the gear carrier 55 through the planet gearing 63 andclutch 5| to-the pump rotorof the hydraulic coupler and thenceto the-turbine rotor 56 of the coupler which is keyed to zthe driven "shaft 56. The. third path is from. the gear carrier .55 through the planet gearing-63; sun .gear 62, clutch 5|, and pump rotor 6| of the hydraulic coupler and to the turbine rotor 56 of the hydraulicconverter which is keyed to the driven shaft 56.- I -An overdrive may be obtained by completely disconnecting the clutch 51 and applying. the brake 56, thus effecting an all-gear overdrive, the ring gear 51 overrunning the gear carrier.

Further modifications will be apparent to those skilled in the art and it is desired, therefore, that the invention be limited only by the scope of the appended claims.

Having thus described my invention, what I claim and desire to secure by Letters Patent is:.

1. A hydraulic gear construction com-prising a .The pump rotor 66 of the hydraulic cou-f pleris connected to rotate with the pump rotor rotary drive member, a liquid torque transmitter including a vaned drive rotor driven from said drive member and avaned driven rotor driven from said vaned drive rotor, a liquid transmitting torque-transmitting rotor extending across the space between said vaned rotors, a first gear means driven from said driven vaned rotor, a second gear means driven from said liquid-transmitting rotor, means for placing said liquidtransmitting rotor into and out of driven relation with respect to said rotary drive member, and means for holding it against rotation in at least one direction when not in said driven relation.

2. A hydraulic gear construction comprising a rotary drive member, a liquid torque transmitter including a vaned drive rotor driven from said drive member and a vaned driven rotor driven from said vaned drive rotor, a liquid-transmitting torque-transmitting rotor extending across the space between said vaned rotors, a first gear means driven from-said driven vaned rotor, a second gear means driven from said liquid transmitting rotor, means for placing said liquidtransmitting rotor into and out of driven relation with respect to said rotary drive member, means for holding it against rotation in at least one direction when not insaid driven relation, and a third gear means driven from both said first and second gear means.

3. A hydraulic gear construction comprising a rotary drive member, a liquid torque transmitter including a vaned drive rotor driven from said drive member and a vaned driven rotor driven from said vaned drive rotor, a liquid-transmitting torque-transmitting rotor extending across the space between said vaned rotors, a first gear means driven from .said driven vaned rotor, a second gear means driven from said liquid-transmitting rotor, means for placing said liquidtransmitting rotor into and out of driven relation with respect to said rotary drive member, means for holding it against rotation in at least one direction when not in said driven relation, means for freeing said first gear means from driven relation with respect to said driven vaned rotor, and means for holding said first gear means against rotation in at least one direction when not in said driven relation.

4. A hydraulic planetary transmission comprising rotary drive means, pump rotor means driven by said drive means, turbine rotor means driven by said pump rotor means, a gear carrier, planet gearing carried by said gear carrier, a first gear meshing with said planet gearing, a second gear meshing with said planet gearing, means for connecting said first gear in driven relation to said turbine rotor means and for disconnecting it therefrom, anchorage means for holding said first gear against reverse rotation with respect to the direction of rotation of said turbine rotor means when disconnected therefrom, means for connecting said second gear for rotation in driven relation to said drive means and for disconnecting it therefrom, and anchorage means for holding said second gear against reverse rotation with respect to the direction of rotation of said drive means when disconnected therefrom.

WILLARD L. POLLARD.

bEnTIFIcATE' OF CORREC'I'iON.

Patent no; 2,522,251. June 22, 1915.

WILLARD L. POLLARD.

It is hereby certified. that error appears inthe printed sneoificationof the above numbered patent requiring correction as follows: Page 1, first I column, line 51, for "rotod". read --rotor--; line 55, strike out "and planetary shaft 9";and thatv the said Letters Patent should be read with this correctiontherein that the same may conform to the record of the case in the Patent Office.

Signed and sealed this 10th day of August, A. D. 1915.

Henry Van Arsdale, (Seal) Aoting Commissioner of Patents. 

